US2648894A

US2648894A - Cutter for producing gears

Info

Publication number: US2648894A
Application number: US769725A
Authority: US
Inventors: Wildhaber Ernest
Original assignee: Gleason Works
Current assignee: Gleason Works
Priority date: 1947-08-20
Filing date: 1947-08-20
Publication date: 1953-08-18
Anticipated expiration: 1970-08-18

Description

Aug. E8, 3953 WILDHABER 2,648,894

CUTTER FOR PRODUCING GEARS Filed Aug. 20, 1947 3 Sheets-sheaf. l

26 :0 F56. 4 lz fi i q \l zz ia n ERNEST WILDHABER Zmnentor 1953 E. WHLDHABER 2,648,894

CUTTER FOR PRODUCING GEARS Filed Aug. 20. 1947 3 Sheets-Sheet 2 ERNEST W I LDHABER 3nventor (Ittorueg 8, 1953 E. WILDHABER 2,648,894.

CUTTER FOR PRODUCING GEARS Filed Aug. 20. 1947 3 speeis-s'neet 5 ERNEST WILDHABER 3nventor FIG. 9 4

\ I g Gttorneg Patented Aug. 18, 1953 CUTTER FOR. PRODUCING GEARS Ernest Wildhaber, Brighton, N. Y., assignor to Gleason Works, Rochester, N. Y., a corporation of New York Application August 20, 1947, Serial No. 769,725

6 Claims.

The present invention relates to tools for and to a method of cutting gears, and more especially to tools for and a method of cutting longitudinally curved tooth, gears, such as spiral bevel and hypoid gears.

Because of advantages in machine construction, when both members of a pair of spiral bevel or hypoid gears are to be generated, it is conventional practice to generate the gears conjugate to nominal crown gears (gears having plane top surfaces and a pitch cone angle of somewhat less than ninety degrees). Where face-mill cutters having straight side-cutting edges are employed as the cutting tools, as is conventional practice, this presents the problem of eliminating bias bearing in the mating gears. The pinion has to be cut one side at a time with its position shifted between cuts, or some special generating motion entailing a special machine is required.

Moreover, whether both members of the pair are generated, or one is form-cut and the mate generated conjugate thereto, cutters having sidecutting edges differently inclined to the cutter axis have been required for cutting gears of diiierent spiral or different dedendum angles. Furthermore, to obtain the localization of lengthwise tooth bearing that is required to enable the gears to accommodate themselves to the variations in loads and mountains that are encountered in use, the mating tooth surfaces of gear and pinion have to be cut with difierent radii of lengthwise tooth curvature. which has heretofore ordinarily meant that for this additional reason different cutters have had to be employed in cutting gear and pinion; and in practice it has ordinarily meant, moreover, that while both sides of a tooth space of the gear might be cut simultaneously, only one side of a tooth of the pinion could be cut at a time.

While these various requirements are not of any particular disadvantage where gears of a particular size, with specific spiral and dedendum angles are to be produced in quantity, the large investment in cutters required and the various problems in production, that have to be met, have discouraged the small shops, which are required to out gears of a wide variety of sizes, and of spiral and dedendum angles, in small lots, from going into the production of spiral bevel and hypoid gears.

Various efiorts have been made in the past to devise satisfactory and practical methods for cutting spiral bevel and hypoid gears in small job lots where the number of cutters required to cut a range of gears would not be too great.

all

One drawback of such so-called Jobbing systems as have heretofore been proposed, however, is that they were only suited to small-lot work. If it became necessary to cut a particular pair of gears in quantity, usually the smalllot system was no longer practical, and new cutters had to be procured and a different method of cutting employed.

With such methods as have heretofore been used, moreover, for cutting spiral bevel and hypoid gears whether in production lots or small quantities, it has been the practice to cut the pinion or smaller member of the gear pair one tooth side at a time to secure the desired localization of tooth bearing; and different cutters have been required for cutting gear and pinion. Methods are known whereby two tooth surfaces of a gear and pinion may be cut at a time, but these require use of special motions or result either in gears of somewhat inferior quality or require separate cutters for gear and pinion. Furthermore, unless special motions are employed, such methods do not always lend themselves to the production of gear pairs having localized lengthwise tooth bearing or contact on mating tooth surfaces.

Where the gears to be produced are pairs in which one member is form-cut and the other generated, conventional methods require a different cutter for the pinion from that used in cutting the gear, for the additional reason that either a female cutter is required on the pinion if a male cutter is used on the gear and both members are to have two tooth sides cut simultaneously, or the included angle between opposite side-cutting edges of the pinion cutter must be smaller than such included angle for the gear cutter if male cutters are to be used in cutting both members.

A primary object of the invention is to provide cutters for cutting longitudinally curved tooth gears which will permit the use of a simplified system of tools so that, with a relatively small number of face-mill cutters, gears of a wide range of tooth numbers, face-widths, pitches, and spiral angles may be out.

Another object of the invention is to provide cutters for cutting longitudinally curved tooth tapered gears with which both members of a gear pair may have opposite sides of each tooth space out simultaneously without bias bearing.

A further object of the invention is to provide cutters for cuttin longitudinally curved tooth gears with which both members of a gear pair may have opposite sides of each tooth space out simultaneously, yet have localized lengthprofiles to have less than full length tooth con-.

tact.

A still further object of the invention is to, provide cutters for cutting longitudinally curved tooth gears with which the two sides of a tooth space may be cut simultaneously in both members of a gear pair with the same tool and yet localized tooth bearing both lengthwise and profile-wise may be obtained on the mating tooth su .ia es.-.

A further object of the invention is to provide cutters for cutting longitudinally curved tooth sears with which the same face-mill cutter may be used in cutting both members of a gear pair.

Still another object of the invention is to provide cutters for cutting longitudinally curved tooth gears with which the same face-mill cutter may be used. cutting vario ars r r ss. o their p al r deden m. an les.

A turther object of the invention is to provide 1 cutter-sv for cutting longitudinally curved tooth gears with which the same cutter may be used for cutting both members of a gear pair and yet both sides of; each tooth space of both members of the pair may be cut simultaneously, not only in ca es where both gears are generated out also where one gear is form-cut and the other generated.

Qther objects, ofthe invention will be apparent hereinafter from the specification and from the recital of' the appended claims.

In the drawings:

Fig. 1; is an axial sectional view of a face-mill cutter? made according to one embodiment of this invention and. constituting one member of a set of cutters that may be employed for cutting a whole range of gears, and showing certain features f. o uc ion of th s u r;

Fig; 2 a, fragmentary axial sectional View. of another. cutter of the set, and illustrating diagrammatically its structure and proportions;

Fig. 31s a, similar view illustrating still another cutter ofthe set and showing further diagrammatically the structure of this cutter and certain features, on which the invention is based;

is a fragmentary sectional view taken at right angles to. the axis of the cutter of Fig. 3 and illustrating one way in which it may be made;

Fig. 5 is a diagrammatic view illustrating certain relationships between the work and the cutter in the generation of the pinion or smaller member of, a gear pair according to this invention;

Fig. ;6. isa fragmentary axial sectional view of a cutter such as may be used in the generation of the pinion of Fig. 5. and illustrating diagrammaticallycertain relationships between the cutteraiidthe work Fig. 7 is a fragmentary axial sectional view through the work axis and the axis of the basic generating gear, illustrating diagrammatically certain relationships between the work and the basic gear ingeneration of one member of a gear pair according to this invention when both members. of the pair have equal tooth dedenda;

Fig. 8 is. a corresponding View showing. the relationships that exist between the work and the basic generating gear in the generation of the pinion or smaller member of a gear pair which have unequal dedenda;

Fig. 9 is a diagrammatic view illustrating the relationship of the work and basic gear in the generation-of the gear or larger member of this latter pair;

Fig. 10 is a diagrammatic view showing certain aspects of the structure of a non-generated gear;

and

Fig. 1-1 is a diagrammatic view illustrating how the present invention may be employed in the production of the mating pinion.

The present invention is based on the use of a novel set of face-mill gear cutters which vary in point-width. These cutters have cutting profiles that are circular arcs and they therefore resemble spherical face-mill cutters. They differ from true spherical cutters, however, in that the centers of curvature of both the outside and the inside cutting surfaces are displaced from, that is, off-set from the axis of the cutter. With these cutters, however, as with spherical cutters, all problems regarding bias bearing are eliminated. Figs. 1 to 3 inclusive show three cutters of a set such as may be employed in this invention.

Referring first to Fig. 3, H3 denotes, a face-mill cutter made according to one embodiment of this invention and comprising the head; Hand a plurality of annularly arranged cutting blades i2". The blades l2 may be secured; to the cutter head the usual way by bolts 93 and may be adjusted" radially of the axis it of; the head in the conventional manner by use. of shims t5 and wedges it. In the view of Fig. 3, for the sake of casein explanation the single blade l2is shown as'having both an, outside cutting edge or profile 2i and an inside cutting edge or profile 2i. The cutter maybe made, and sharpened. however, in-conventionalmanner so that alternate blades have opposite side-cutting edges, as shown in Fig. 4.

2i? and 25 are the actual cutting edges of the blade or blades ifthe cutting edges are located in an axial plane of the cutter. They denote the cutting profiles of the cutter if'the actual cuttinged as are off-set from an axial plane. They are then the profiles of an axial section of'the'surfaces described by the cutting edges as the cutter rotates on its axis I l.

By cutting surfaces, then, as used hereinafter are meant the surfaces of revolution described bythe cutting edges as they rotate about the cutter axis.

The outside cutting profile is a convex circular are centered at 22. The inside cutting profile 2! is a concave circular are centered at 23.

t will be noted that both

centers

22 and 23 are off-set from cutter i i. Ina true sphericalcutter, the centers of the outside and-inside cutting profiles would be on axisit and for cutting profiles of the inclinations or pressure angles shown would.- be at and- 25; respectively. It will be seen, then, that the radius of the outs-idec-ueting profile'ZEiof the cutter it! is larger than the profile radius of a spherical-surface of the sameinclination, while the inside cutting profile 2|. has a smaller radius than. a spherical cutting profile of equal inclination. The outside cutting edges of the cutter Iii are; therefore, less convexancl will remove. therefore, slightly more stock. at. the top and bottom of the profile of, a-gear tooth-cut. by the cutter, than a cutter. having a, true spherical outside cutting surface. Likewise theinside. cutting, profile. of. the cutter shownis. more: concave than would be the inside cutting surface of a true spherical cutter and will remove more stock at the top and bottom of a tooth profile than a true spherical cutting surface. The cutter ID has, therefore, the ability to produce a tooth shape on the work which may mesh with its mate gear with less than full profile contact.

It is known that some easing off in tooth profile contact may be had in a pair of gears cut with cutters of circular arcuate profile shape by making the cutters so that their centers of curvature are off-set from the cutter axis. The novelty of the cutters of the present invention resides in the positions of the

centers

22 and 23 of profile curvature with respect to the cutter axis and in the relative proportions of the cutting profile to the cutter point-widths.

In the cutter H3 shown in Fig. 3, the profile centers 22 and 23 are spaced from cutter axis 54 at distances which are proportional to their

respective profile radii

26 and 21. A straight line 28 connecting the

centers

22 and 23 is inclined at an angle a to the cutter axis 14 and it intersects the cutter axis at a point Distances 22-0 and 23-9 are also found to be proportional to the radii 23, 2?. It will be apparent, then, that any line passing through point 0, such as the dotted line 29, will have the same inclination to the cutting profiles 29 and 2 I. In other words, the pressure angles of the cutting profiles 20 and 2! are equal with reference to a line 29 passing through point 0 and intersecting these profiles. This is the case because the normal distances of

points

22 and 23 from line 29 are proportional to the distances 22-0 and 23-O and are therefore proportional to the profile radii 26 and 2?. The sine of the pressure angle is equal to the proportion of the distance of the point 22 from line 29 to the radius 26 for the outside cut-, ting profile; and for the inside cutting profile, the sine of the pressure angle is equal to the proportion of the distance 23 from line 29 to the radius 2?. The two sines and pressure angles are alike because the two proportions are equal. Any other line passing through 0, such as the line 29' is also equally inclined to the two cutting profiles 20 and 2!. The practical advantage of this design of cutter will appear hereinafter.

The cutters of Figs. 1 and 2 are similar in structure to the cutter of Fig. 3. They difier, however, from the cutter of Fig. 3 in point-width, that is, in the distance between opposite sidecutting profiles of the cutter at the tip of the cutter. For a cutter, each of whose blades have opposite side-cutting edges, the point-width is the width of a blade at its tip. For a cutter, such as shown in Fig. 4, in which alternate blades have opposite side-cutting edges, the point-width is the distance between opposite side-cutting edges measured across the tips of two successive blades.

The cutter 30 of Fig. 1 has a smaller pointwidth 3! than the point-width 4| of the cutter 40 of Fig. 2, and the cutter 40 of Fig. 2 has a smaller point-width 4! than the point-width of the cutter iii of Fig. 3. The

cutters

30 and 40 have, however, the characteristic that the centers of their outside and inside cutting profiles are off-set from their axes and the ofi-sets are in proportion to the radii of the cutting profiles.

Thus, in the cutter 30 of Fig. 1, the outside cutting profile 32 has its center at 34 and the inside cutting profile 33 has its center at 35, and the distances of the two centers 34 and 35 from the cutter axis 36 are in proportion to '6. the radii 38 and 39 of the two cutting sun faces. Furthermore, the two centers 34 and lie on a line 52 which intersects the cutter axis 36 in a point 0' which is spaced from centers 34 and 35 in proportion to the radii 38 and 39. Moreover, the cutting profiles 32 and 33 are equally inclined to any line 3'! drawn through point 0' and intersecting the profiles.

Likewise, the outside cutting profile 42 and the inside cutting profile 43 of cutter have centers 44 and 45, respectively, off-set from the cutter axis 43 distances which are proportionate to the

radii

43 and 49 of these profiles. Moreover, the line 54 connecting the centers 44 and 49 intersects the cutter axis 46 in a point 0 which is spaced from centers 44 and distances which are proportionate to the

radii

48 and 49, respectively. Furthermore, the outside and inside cutting profiles 42 and 43 are equally inclined to a line 41 which passes through point 0''.

It should be noted that the angle a of inclination of the line,'52, 54, or 23, which connects the profile centers, to the cutter axis, 36, 46, or [4, decreases with increasing point-width, and that the point, 0, O, or O, of intersection of this line with the cutter axis is displaced axially forward of the cutter axis with increasing pointwidth of the cutter. Points 0 and O are beyond the tips of the blades in the cutters of Figs. 2 and 3, while point 0' is below the tips of the blades of the cutter of Fig. 1, and the point 0 is more beyond the tips of the blades of the cutter or Fig. 3 than point 0 is beyond the tips of the blades of the cutter of Fig. 2.

Angle a is a factor related to ease-off or modification of the tooth profile of the gear, which is cut with the cutter, at the top and bottom thereof. With my system of cutters, the profile easeoff at the tooth depth proportional to the cutter point-width is either constant or increases moderately with increasing point-width.

The cutters shown will produce not only tooth surfaces on mating gears which have less than full profile contact, but also tooth surfaces which have less than full length contact. The lengthwise ease-ofi or localization of tooth bearing is controlled by the radius of lengthwise curvature of the cutter. The cutter [0 of Fig. 3 sweeps out lengthwise tooth surfaces which have a lengthwise radius of curvature equal to radius 26 minus distance 2224, point 24 being the center of lengthwise curvature of the cutting surface and of the longitudinally concave tooth surface produced by the cutter. In similar manner, the inside cutting surface of the cutter sweeps out a tooth surface whose lengthwise curvature equals profile radius 21 plus distance 2325, point 25 being the. center of lengthwise curvature of the longitudinally convex tooth surface swept out by inside. cutting profile 2|.

It will be seen that the radius r of lengthwise curvature of the cutter is larger for the outside cutting surface than for the inside cutting surface. The difference decreases with increasing point-width. Thus, the cutter 30. of Fig. 1 gives more ease-off at the outer and inner ends of the tooth surface and produces a shorter lengthwise tooth bearing than do the cutters shown in Figs. 2 and 3.

A further feature of my system of cutters is the control of lengthwise tooth bearing by shimming the cutter blades. This applies, of course, only where the cutter has separate outside and inside cutting blades, as has the cutter of Fig. 4. In such case, the cutting point-width 3|, 4|

or 5.4 can. be cha es hr eei st he t e; uties: nd. ns de blades ac a l ew awa there one nothe hus. i it. s. he; hat a cut er of the o nt-width 4H. a. 2; P du es a pa r. mati ears. en thwise tQQih h a i es. or ntact on. me hin t th. ehrieeee ha re too, hor the ee h b a n s eh h len thened y us n the utter it if g.3 eth r 5. 3 41 mi e it blad ted-nee ts e t hei ahitisit to the noih rw d h 4:1. .01. eehi e 9 hi resu tis iu tn he .d fie r re i e shi t adi of th cuttin urf a ed e Quilter o diff nt heihtewhi h i y m u ters.

i s- 5 nd. 6 i l stra dia ammat cally h w the utte s of thep s ht i y ion ma he u e in the n ratio Qf a hai o e rs; rem bas crow ars o omi al r waeea r 6.0- en tes h e -1e. e reem ht l eh i. 61 i a .tqeihei s ea hat is a t o h. su h, as wil be. tiecr bed b a u t made eeeerd hg: o th nv n on h w of his 5 is. a see en n rhen ieh a to h a 62 o the c own. seer ehe mid. the height of the teeth of the crown gear. pinion a which s to e ut. i cl heted dotted lines at 56 designates the axis of h P n n nd i s ehe Th ne l es Oh e b c. g a axis .62- The ax ll of the wtter intersects the plane of Fig. 5 at point. 01, which has a position on the cutter axi corre n t hep ih 9 Qt i 3- P is a me n point el he the he Q ih t et it Fi 6 is a herme xe ieh. ehen al n t li .e.f -?i.eaha eehteihh-ie he f t r it h .ee rs p th ut ide and; nsi e -t m hri e of the gu te e a 14 and, 5. e eer e a. aeee dih t9: t e .h ihe h e herein a d el whlF th-2e e e er e jereh th same depth regardless of the tooth combination,

at least "if the gears have full dpth teeth and. are designed foragiven point-widthcutter. The cutter position in'the normal planec'anl therefore readily be tabulated for the whole listoi cutters. The. gear or pinion to be -cut-may be generated accordingto conventional'practice by rotating the cutter on its axis H while rolling cutter and work relative to one another" as though the work were meshing 'with' the'lqasic generating gear, as, for instance, by rotating the work on its axis 5,6 while efiecting relative' swing of cutter and work. about the axis 62 the basic gear.

Figs. 7 to 9 ,areaxial sections taken through the work axis and the axis of the crown gear and showing the generation of other gears by the system of thepresentinvention. Fig. '7 i1-, lustrates the cutting of a mitre gear .913, whose mate is the piniontfi. Plane is again the pitch plane of the basic crown gear represented by the cuttenwhich may be the samecutter H1 as used in cutti pinion 6,5. Herethededencl Y ang e o b equa n. airmen h e of the sear p i ae d t rm ned from. therequ m htthet the pirela ele h sam 91 nvention, the cutter is so posihe heideeen 4- or tha -ear e1. the: eat. earh computation of th dedehehhi ehele i KQQ R h 61 h ea pex i -5Q H denotes the position of thecutter axis projection.

For cutting the two members or the painpret erably the same cutter is used For reasons of y metry ith respect to p n 0 he ncl nation of the cutter axis H to said plane and to the axis 62 of the basic crown gear or cradle is madethe same in cutting both members of the gear pair. The distance. of the cutter axis from the axis of the crown gear or cradle is; alsothe.

same on both members, and so is the position ofthe cutter lengthwise o f the cradle axis. A minimum of time is, therefore, required to set the gear cutting machine over from cutting one. member of the gear pair to the other. Also, if there is a slight difference in the distance t; the cradle axis from the cutter axis as com with a specified computed value, this difierenge; exists on both members so that one difierenoc, compensates the other.

It is known that a pair of bevel gears areqgn; jugate to each other when they are conjugate to the two members, respectively, of a ir of; complementary basic gears whose axis passes; through the apex of said pair of hovel gears These complementary basic gears have .ratigs; such as to roll on the pitch cones of said bevel; gears. The basic crown gear represented by the cutter and having its axis at 63 which is usedin the generation of gear and the basiccrown gear used in the generation of the mating gear are symmetrical with respect to pitch plane St. The crown gears are exactly complementary when the teeth have full lengthwise tooth bearing. They can still be called complementary when less than full length tooth bearing is built into the cutters. Thus, with the present invention gears 95 and 9!! canbe generated conjugag to one another and with the samecutterlfl,

With the present invention these outstanning advantages are retained, also, cutting gears which have unequal dedenda. A similarpair of, basic gears is used. This is illustrate 8 and 9, which show, respectiyely, the genera: tionof a pinion Hi0 and of a mating gear till, T he'two complementary basic gears are metrical with respect to plane 8%. Thus, the root line I02 of the pinion [Q0 is inclined at the same angle Hill to the plane 80"as the root line l03 of the mating gear 101.. The two root lines 102 and Its intersect at a point teayuie f e lines of the two gears intersect at point a long tooth addendum is obtained on pinion by inclining its pitch line. element ill-lite, the plane of symmetry filt. Preferably the pitch line element IQ! is made to pass through point It intersects the axis .62 of the basic ,gearat the apex or cone center. 5.8. $9 clenotesjhe axis of the pinion t9 and lit the axisofthefgear T: Note that their common apex)?! is offset from the plane of symmetry 80'. x

In generation of either member of the pair, thecutter is rotated on its axis 'Hin engage; ment with the work while a relative. rolling move: ment is producedbetween the cutter and work about the axis of the basic gear. Inthis rolling movement, the cutter represents, as usual, a toothof the basic gear. The rolling movement, may be efijected by rotation of the work on its axis 199 or us while the cutter is swung relative to the work about the axis 62' of the basic gear. In generation, the pitch cone of the Pinion HID rolls on the pitch surface of the basic gear, which is a cone obtainable by rotating element I01 about axis 62'. Its pitch angle I I2 is larger than a right angle by the difference between the average dedendum angle I04 and the dedendum angle of the pinion. This difference is the dedendum angle increment of the gear. Angle H2 is a right angle plus the dedendum angle increment. Pitch angle I I3 of the complementary basic gear used in the generation of the gear IOI (Fig. 9) is a right angle minus the dedendum angle increment.

The two gears of any gear pair I and IDI having unequal dedenda may be cut with the same cutter with a minimum of effort. The setup of the cutter in the cradle is much like the set-up of Fig. 7 and much of it can be tabulated. The set-over from one member of the pair to the other is simple and requires no change in the cutter tilt and no change in the radial distance of the cutter axis from the axis 62' of the cradle. The two basic gears thus used, with their plane of symmetry 80, solve perfectly the problem of conjugacy of the gears I00 and I 0| The present invention is applicable not only where both members of a gear pair are generated but also to the cutting of the generated member of a gear pair where the other member is form-cut or non-generated. In this latter case, the pinion is generated conjugate to the form-cut gear by providing a cutter which describes a gear tooth and by rolling the gear represented by the cutter with the pinion blank.

Fig. 10 can be considered a normal section through a form-cut gear I20. The pitch circle of this gear is indicated at I2I. Its tooth spaces I22 are cut as counterparts of the cutting surfaces of the cutter. Thus the sides I23 and I24 of the gear teeth are essentially portions of convex and concave spherical surfaces, respectively.

If one side I24 of a tooth is turned about the axis of the gear I through the angle of a normal pitch of the gear, the correspondin side I24 of the next tooth may be obtained. Side IZG' has less inclination to side I23 than side I24, the included angle I25 between opposite sides I23 and I24 of a gear tooth being less than the included angle I26 between opposite sides of a tooth space on form-cut gears. In the known procedure, the cutter which cuts the pinion and which describes the tooth of the gear has, therefore, a smaller included angle I25 between its opposite side-cutting edges than the gear cutter which describes a tooth space of the gear. While gear cutters may be made standard, as in conventional practice, a great variety of pinion cutters is therefore, required.

The present invention permits use of a reduced number of pinion cutters. With the present invention, either the same cutter may be used on both gear and pinion or cutters with the same included angle. The included angle of the pinion cutter is then larger than the angle between opposite sides of the teeth of the non-generated gear. This difference is made up in the generation of the pinion. Instead of rolling the pinion on its pitch circle I3I (Fig. 11) it is rolled on a larger circle I32, and the pinion blank and cutter are rolled on this larger circle I32 as though the pinion were rolling with a gear whose pitch circle is at I33 concentric with the axis of the gear but inside the pitch circle I2I of the gear. In practice, this means reducing the ratio of roll below the ratio of the tooth numbers of gear and pinion. On spiral bevel or hypoid pinions, a S t ge of spiral angle is also required. The changes can be computed or determined experimentally in the shop. In view of the small changes involved it is not difiicult to find what they are by trial. In this manner a substantial saving in cutter equipment is achieved and the right cutters are always on hand.

IE4 is the axis of the gear, and I35 is the axis of the pinion. I36 and I31 denote, respectively, the profiles of opposite side-cutting surfaces of the cutter used in generation of the pinion. The included angle between these opposite side-cutting surfaces is denoted at I38 and is equal to the included angle I26 between the opposite sides of a tooth space of the gear, that is, to the included angle between the opposite side-cutting surfaces of the gear cutter.

While the invention has been described in connection with certain particular embodiments thereof and in ccnnection with certain uses therefor, it will be understood that it is capable of further modification, and that this application is intended to cover any variations, uses, or adaptations of the invention following, in general, the principles of the invention and including such departures from the present disclosure as come within known or customary practice in the art to which the invention pertains and as may be applied to the essential features hereinbefore set forth and as fall within the scope of the invention or the limits of the appended claims.

Having thus described my invention, what I claim is:

l. A face-mill gear cutter having outside and inside cutting surfaces that are of curved profile shape in a plane axial of the cutter and that have different radii of profile curvature, the centers of profile curvature of said surfaces being off-set from the axis of the cutter and the amounts of off-set of said centers being proportional to the radii of profile curvature of the respective surfaces.

2. A face-mill gear cutter having outside and inside cutting surfaces that are of convex and concave circular arcuate profile shape, respectively, in a plane axial of the cutter and that have different radii of profile curvature, the centers of profile curvature of said surfaces being off-set at opposite sides of the axis of the cutter and the amounts of off-set of said centers being proportional to the radii of the respective surfaces.

3, A face-mill gear cutter having outside and inside cutting surfaces that are of convex and concave circular arcuate profile shape, respectively, in a plane axial of the cutter and that have different radii of profile curvature, the centers of profile curvature of said surfaces being off-set at opposite sides of the axis of the cutter so that a line drawn through said centers is incllned to and intersects said axis, and said cutting surfaces being equally inclined to any line drawn through the point of intersection of the line of centers with said axis.

4. A face-mill gear cutter having outside and inside cutting surfaces that are inclined to the cutter axis and that are of curved profile shape in a plane axial of the cutter and that have different radii of profile curvature, the centers of profile curvature of said surfaces being offset from the axis of the cutter, the radius of profile curvature of the outside cutting surface being larger than the radius of profile curvature of a spherical asses-94 surface which is centered on the cutter axis and is at the same distance from and is of the same inclination to the cutter axis, the radius of profile curvature of the inside cutting surface being smaller than the radius of profile curvature of a spherical surface which is centered on the cutter axis and is at the same distance from and is of the same inclination to the cutter axis, and the amounts of offset of said centers being proportional to the radii of profile curvature of the respective surfaces.

5. A rotary face-mill gear cutter having outside and inside cutting blades that are adjustable radially of the cutter axis, said blades having out-side and inside cutting edges that lie, respecti'vely, in cutting surfaces that are, respectively, of convex and concave circular arcuate profile shape in a plane axial of the cutter, and that have different radii of profile curvature, respectively, the centers of profile curvature of said surfaces being offset, respectively, at opposite sides of the axis of the cutter and the amounts of offset of said centers being proportional to the radii of the respective surfaces in one position of radial adjustment of the blades.

6. A rotary face mill gear cutter having outside and inside cutting surfaces that are of convex and concave circular arcuate profile shape, respectively, in a plane axial of the cutter, and

that have different radii of profile curvature, the centers of profile curvature of said surfaces being offset at opposite sides of the axis of the cutter so that a line drawn through said centers i inclined to and intersects said axis, and said cutting surfaces being equally inclined to any line drawn through the point of intersection of the line of centers with said axis, the outside cutting surface having a greater radius than the inside cutting'surfiace.

ERNEST WILDHABER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name 7 Date 1,364,056 'Farnum 111., Dec. 28, 1920 1,654,199 Wildhaber Dec. 27, 1921 1,655,080 Wildhaber Jan. 3, 1928 1,97 ,135 Adams Sept. 11,1934 2,114,793 .Bauersfel'd Apr. 19., 1938 2,346,806 Wildhaber Apr. 18, 1944 2,346,807 Wildhaber Apr. 18, 1944 2,353,768 Shlesin'ger July 18, 1944 FOREIGN PATENTS Number Country Date 546,494 Great Britain July 16,1942